CN101963418B - Micro channel heat exchanger for air-conditioner heat pump - Google Patents
Micro channel heat exchanger for air-conditioner heat pump Download PDFInfo
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- CN101963418B CN101963418B CN200910157622A CN200910157622A CN101963418B CN 101963418 B CN101963418 B CN 101963418B CN 200910157622 A CN200910157622 A CN 200910157622A CN 200910157622 A CN200910157622 A CN 200910157622A CN 101963418 B CN101963418 B CN 101963418B
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Abstract
The invention discloses a micro channel heat exchanger for an air-conditioner heat pump. The heat exchanger comprises an upper head pipe, a lower head pipe, a plurality of flat pipes and a plurality of fins, wherein the upper head pipe is parallel with the lower head pipe; the plurality of flat pipes connect the upper head pipe and the lower head pipe and are parallel at intervals; opening holes communicating with the insides of the upper head pipe and the lower head pipe are reserved in the flat pipes; the plurality of fins are arranged between adjacent flat pipes along the length direction of the flat pipes; and the distribution density of the fins is reduced gradually from the upper head pipe to the lower head pipe along the length direction of the flat pipes. According to the micro channel heat exchanger, the air side heat transfer coefficient of the heat exchanger can be improved and the air side flow resistance can be reduced; and the surface tension born by condensate water on the surfaces of the flat pipes is low both under cooling and heating working conditions and the condensate water is hard to stay in gaps of the fins, so that the wind resistance is reduced and heat transfer is not influenced, the discharge of the condensate water is improved, and frost formation is also improved at the same time.
Description
Technical field
The present invention relates to the cold and hot switching technology of air-conditioning, the micro-channel heat exchanger that particularly a kind of air-conditioning heat pump uses.
Background technology
At present, heat pump type air conditioner is a kind of air conditioner that often uses.When freezing summer, air-conditioning is in indoor refrigeration, outdoor heat radiation, and when heating in the winter time, direction is opposite with summer, i.e. indoor heating, outdoor refrigeration.Air-conditioning carries out cold and hot exchange through heat pump between varying environment.Such as in the winter time, outdoor air, the surface water, underground water or the like are exactly low-temperature heat source, and room air is exactly a high temperature heat source, the effect that heat pump air conditioner heats be exactly the heat delivery of outdoor environment in indoor environment.
With reference to shown in Figure 1, what show a kind of heat pump in the prior art heats circulation theory figure.This heat pump comprises: evaporimeter 1, compressor 2, condenser 3, expansion valve 4 and four-way change-over valve C.The concrete course of work that this heat pump heats is: at first, the two phase refrigerant of low-temp low-pressure (amalgam of liquid phase refrigerant and vapor phase refrigerant) absorbs the heat of cryogenic object in evaporimeter 1, flashes to the gas refrigerant of low-temp low-pressure; Then, this low-temp low-pressure gas refrigerant is compressed to the gas refrigerant of HTHP after compressor 2 sucks; Then, the gas refrigerant heat release in condenser 3 with said HTHP discharges heat energy to hot environment, self becomes the cryogenic high pressure liquid refrigerant simultaneously; At last, this cryogenic high pressure liquid refrigerant reduces pressure in expansion valve 4, becomes the two phase refrigerant of low-temp low-pressure, gets into evaporimeter 1 once more, repeats the process that heats of above-mentioned circulation.Above-mentioned evaporimeter 1 is heat exchanger.
Heat pump air conditioner changes the operating mode pattern through this four-way change-over valve C.Under the summer cooling condition, indoor heat exchanger is exactly an evaporimeter 1, and outdoor heat converter is exactly a condenser 3.The room air cooling that is cooled through evaporator 1 surface reaches the purpose that indoor temperature is descended, and heat is transported to outdoor through condenser 3, take away through circulating air.In the time of Winter heat supply, switch with four-way change-over valve C, the air intake duct of heat pump and the position of blast pipe are exchanged, and then the flow direction of cold-producing medium is changed, at this moment, indoor heat exchanger is exactly a condenser 3, and outdoor heat exchanger is exactly an evaporimeter 1.Above-mentioned like this heat pump can be realized the purpose that heats in outdoor heat absorption to indoor heat release.
Evaporimeter 1 is the equipment of output cold, and its effect is to make the refrigerant liquid evacuator body that flows into through expansion valve 4, with the be cooled heat of object of absorption, reaches the purpose of refrigeration.Condenser 3 is the equipment of quantity of heat given up, and the heat that the heat that from evaporimeter 1, absorbs is transformed together with the compressor 2 consumed works medium that in condenser 3, is cooled is taken away, and reaches the purpose that heats.Evaporimeter 1 is the piths that carry out exchange heat in the air conditioner and heat pump unit with condenser 3; It mainly carries out the exchange of heat through finned tube or by the micro-channel heat exchanger that finned tube is formed; Therefore, the quality of finned tube or the micro-channel heat exchanger performance be made up of finned tube will directly have influence on the performance of whole system.
Illustrated in fig. 2 is the structural representation of micro-channel heat exchanger of the prior art; As known in those skilled in the art, this micro-channel heat exchanger comprises: upper head pipe 11 and lower head pipe 14, the parallel respectively two ends up and down that place heat exchanger; One end of upper head pipe 11 seals; The other end has central through hole as refrigerant inlet 8, and an end of lower head pipe 14 also seals, and the other end has central through hole as refrigerant outlet 9.Upper head pipe 11 and lower head pipe 14 also can be set the direction of cold-producing medium inflow and outflow as required, and promptly cold-producing medium also can flow into as inlet from lower head pipe 14, flow out as exporting from upper head pipe 11 again.Arrow shown in the figure shows the direction of flow of refrigerant.Side at the outer wall of head pipe 11 and 14 equates along having at interval on the tube axis direction, equally distributed fluting 5, fluting 5 and head manage 11 with axis direction vertical, and penetrate tube wall.Between two stature pipes, has multi-disc flat tube 6, following pipe 11 and 14 in the connection.Along the length direction of flat tube 6, be evenly distributed with the perforate (shown in Figure 11 a and 11b) that is parallel to each other in the inside of flat tube 6.Respectively on the insert head pipe 11 and 14 in the corresponding fluting 5, the perforate in the flat tube 6 is communicated with the central through hole of head pipe 11 and 14 two ends of flat tube 6, and with flat tube 6 and manage 11 and be in the same place with 14 junction outer surface soldering.Like this, equate at interval between every adjacent two flat tubes 6, and be parallel to each other, two stature pipes 11 and 14 are linked together.In kind of refrigeration cycle, cold-producing medium just can get into upper head pipe 11 through the refrigerant inlet 8 of upper head pipe, transfers to lower head pipe 14 through flat tube 6 inner perforates, and discharges heat exchanger through the refrigerant outlet 9 of lower head pipe 14.Length direction along flat tube 6 is provided with the fin 7 that a plurality of head and the tail alternately join, and constitutes corrugated fins set, and the distribution of fin is even at interval, and through soldering fin 7 is fixed on the flat tube 6.Fin 7 is used for increasing the heat exchange area of air side, thereby improves heat.
At heat exchanger shown in Figure 2 during as condenser working; The high-temperature high-pressure refrigerant gas that compressor is discharged gets into heat exchanger from refrigerant inlet 8; The central through hole of the upper head of flowing through pipe 11 enters into each root flat tube 6, and cold-producing medium is transferred to the lower head pipe 14 of opposite side through flat tube 6 inner perforates.In transmission course; Cold-producing medium heat release in flat tube 6; Through bolt for fastening a door from outside pipe 6 with its on 7 heat radiations of a plurality of fins, and the Cryogenic air of flowing through in the compartment between the adjacent fins 7 10 carries out heat exchange, liberated heat is taken away by Cryogenic air; High-temperature high-pressure refrigerant in the flat tube 6 then is cooled to liquid state by gaseous state, through outlet 9 outflow heat exchangers of head pipe 14.
In the operation of reality, when source pump heated in the winter time, to the cold wind of going out, because evaporating temperature is lower, the surface temperature of the fin 7 of heat exchanger also descended thereupon as the outdoor heat exchanger of evaporimeter 1.If surface temperature is lower than zero temperature, when outside air was flowed through heat exchanger, the surface that flat tube 6 will separated out and be attached to its contained moisture formed condensed water.Although condensed water receives gravity and the mobile impetus of air; The trend that downward discharging is arranged, but because fin 7 gaps are too small, and because of the reason of flat tube 6 surface irregularities of remaining solder flux; Cause condensed water under capillary effect, can't discharge heat exchanger smoothly.When the evaporating temperature of evaporimeter 1 was lower than 0 ℃, the moisture of separating out in the air will form the frost layer at evaporator surface.The frost layer on condensed water that no matter gathers or surface all can directly reduce the air side heat transfer coefficient of heat exchanger, increases the flow resistance of air side, worsens the performance of unit, reduces the heat capacity of unit.
In view of the above problems, how to solve the condensed water and frost layer phenomenon that occur in the micro-channel heat exchanger, the air side heat transfer coefficient that improves heat exchanger has become problem demanding prompt solution with the flow resistance that reduces air side.
Summary of the invention
Partly introduced the notion of a series of reduced forms at summary of the invention, this will further explain in specific embodiment part.Summary of the invention part of the present invention does not also mean that key feature and the essential features that will attempt to limit technical scheme required for protection, does not more mean that the protection domain of attempting to confirm technical scheme required for protection.
For solving above-mentioned the problems of the prior art; The present invention provides a kind of can improve the air side heat transfer coefficient of heat exchanger and the heat exchanger of the flow resistance that reduces air side; Said heat exchanger comprises upper head pipe and lower head pipe, and said upper head pipe and said lower head pipe are parallel to each other; The a plurality of flat tubes that are parallel to each other and separate that connect said upper head pipe and said lower head pipe, said bolt for fastening a door from outside pipe inside is provided with the perforate with said upper head pipe and said lower head pipe internal communication; Be arranged on a plurality of fins of arranging on the said flat tube length direction in edge between the adjacent said flat tube, the length direction of the distribution density of said fin from said upper head pipe along said flat tube reduces towards said lower head pipe gradually.
According to a further aspect in the invention; A kind of micro-channel heat exchanger that is used for air-conditioning heat pump also is provided; This heat exchanger comprises upper head pipe and lower head pipe; Said upper head pipe and said lower head pipe are parallel to each other; Also comprise the middle size pipe between said upper head pipe and said lower head pipe, and a plurality of first group of flat tube that is parallel to each other and separates that connect said upper head pipe and said middle size pipe, with a plurality of second group of flat tube that is parallel to each other and separates that are connected said lower head pipe and said middle size pipe; Said first group of flat tube inside is provided with first group of perforate with said upper head pipe and said middle size pipe internal communication, and said second group of flat tube inside also is provided with second group of perforate with said lower head pipe and said middle size pipe internal communication; And be arranged on first group of fin arranging on the said first group of flat tube length direction in edge between adjacent said first group of flat tube, and be arranged between adjacent said second group of flat tube along second group of fin arranging on said second group of flat tube length direction.
Compared with prior art, the present invention carries out different arrangements with the density of fin in the heat exchanger in the prior art or flat tube, Size Distribution, and flat tube is adapted as structure wide at the top and narrow at the bottom; No matter in refrigeration or heating condition; The surface tension that the surperficial condensed water of flat tube is received is smaller, is difficult for resting in the fin slit, thereby reduces windage and influence heat exchange; The discharging of condensed water is improved, also can play a role in improving simultaneously frosting.
Description of drawings
Attached drawings of the present invention is used to understand the present invention at this as a part of the present invention.Embodiments of the invention and description thereof have been shown in the accompanying drawing, have been used for explaining principle of the present invention.In the accompanying drawings,
Fig. 1 shows the kind of refrigeration cycle schematic diagram of heat pump of the prior art;
Fig. 2 shows the structural representation of micro-channel heat exchanger of the prior art;
Fig. 3 a shows the structural representation of a kind of heat exchanger of the present invention;
Fig. 3 b is the local fin distribution schematic diagram in I district and II district among Fig. 3 a;
Fig. 4 a shows the structural representation of second kind of heat exchanger of the present invention;
Fig. 4 b shows the flow schematic diagram of the heat exchanger cold-producing medium when refrigeration among Fig. 4 a;
Fig. 4 c shows the flow schematic diagram of the heat exchanger cold-producing medium when heating among Fig. 4 a;
Fig. 4 d shows the flow schematic diagram of the heat exchanger cold-producing medium when defrost among Fig. 4 a;
Fig. 5 shows the structural representation of size pipe connection flat tube among Fig. 4 a;
Fig. 6 shows another kind of heat exchanger structure sketch map of the present invention;
Fig. 7 shows I of the present invention district and II district flat tube another kind of sketch map that distributes on middle size pipe;
Fig. 8 shows the sketch map of flat tube another distribution on middle size pipe in I of the present invention district and II district;
Fig. 9 a and Fig. 9 b show in the heat exchanger of the present invention another flat tube configuration front view and side view on the size pipe;
Figure 10 a and Figure 10 b show the flat tube sketch map of two kinds of different perforate pore-size distributions;
Figure 11 a and Figure 11 b show asynchronous front view of width and side view;
Figure 12 a and Figure 12 b show two kinds of structural representations of fin;
The front view of size pipe and the heat exchanger that adds size pipe in this during Figure 13 a and Figure 13 b show;
Another front view of size pipe and the heat exchanger that adds size pipe in this during Figure 14 a and Figure 14 b show;
The third front view of size pipe and the heat exchanger that adds size pipe in this during Figure 15 a and Figure 15 b show.
Description of reference numerals
1: evaporimeter 2: compressor 3: condenser 4: expansion valve
5,5 ': fluting 6: flat tube 7: fin 8: refrigerant inlet
9: outlet 10: Cryogenic air 11: upper head pipe 12:I district flat tube
13:I district fin 14: lower head pipe 15:II district fin 16: middle size pipe
17:II district flat tube 18: guiding gutter C: four-way change-over valve
The specific embodiment
In the description hereinafter, a large amount of concrete details have been provided so that more thorough understanding of the invention is provided.Yet, it will be apparent to one skilled in the art that the present invention can need not one or more these details and be able to enforcement.In other example,, describe for technical characterictics more well known in the art for fear of obscuring with the present invention.In the accompanying drawing, the parts with same reference numerals are represented identical or akin parts.
Shown in figure 3a and Fig. 3 b, Fig. 3 a shows the structural representation according to a kind of heat exchanger of the present invention, and Fig. 3 b is that fin local among Fig. 3 a is at I district and II district distribution sketch map.Heat exchanger according to present embodiment comprises: upper head pipe 11, be parallel to said upper head pipe 11 lower head pipe 14, connect a plurality of parallel flat tubes 6 that separate of this upper head pipe 11 and lower head pipe 14, and a plurality of fins that separate that are provided with on this flat tube 6.Different with prior art is, fin is not to be evenly distributed on the bolt for fastening a door from outside pipe 6 among the present invention, but fin is set to two different parts of distribution density.Shown in Fig. 3 a, micro-channel heat exchanger is divided into I district (top) and II district (bottom) two parts through cut-off rule A-A ', and is corresponding, and said fin 7 is divided into I district fin 13 and II district fin 15.From Fig. 3 b, can find out, along the length direction of flat tube 6, the gap that the gap that the wave that the fin of said II district fin 15 forms distributes distributes greater than this I district fin 13.
Particularly, in heat exchanger, it is different that I district fin 13 and the Density Distribution of II district fin 15 are set to, and the density of the density of I district fin 13 greater than II district fin 15 is set, and said I district fin 13 is installed on the identical flat tube with II district fin 15.Can find out among Fig. 3 b that II district fin 15 distributes more sparse, for example, about 16～20 slices/inch along the length direction of flat tube 6, then distribution is closeer for I district fin 13, for example, and along on the length direction of flat tube 6 about 20～23 slices/inch.In heating condition, during evaporator operation, the condensed water of generation is because the effect of gravity; Can drip downwards along flat tube 6, so the bottom of heat exchanger can gather many condensed waters, owing to the bottom is that II district fin 15 density are less; The fin gap is bigger, and the surface tension that makes condensed water receive is smaller, is difficult for resting in fin 15 slits, II district; Thereby reduce windage and influence heat exchange, the discharging of condensed water is improved, also can play a role in improving simultaneously frosting.Therefore, the purpose of said structure is to adjust the distribution density of fin, adjusts the fin density of easy frosting part less relatively, makes this part be difficult for gathering condensed water relatively, thereby reduces the influence of frosting heat exchanging.So the Density Distribution of above-mentioned fin is explanation as an example only, is not limited to above-mentioned scope.Similarly; According to conditions such as different working conditions, different heat exchange device sizes; Those skilled in the art can obviously be set to three perhaps parts of more different densities with the fin of heat exchanger in a similar fashion according to above-mentioned embodiment; The density that fin distributes exports the direction that flows along cold-producing medium and reduces gradually from entering the mouth to, reduce easy frosting fin density partly to reach, thereby reduces the purpose of frosting heat exchanging influence.
Shown in figure 4a, show the structural representation of second kind of heat exchanger of the present invention.This heat exchanger comprises: upper head pipe 11, be connected with middle size pipe 16 through I district flat tube 12; Middle size pipe 16 is connected with lower head pipe 14 through II district flat tube 17 again.I district flat tube 12 is provided with a plurality of I district fin 13, and II district flat tube 17 is provided with a plurality of II district fin 15.Different with the head pipe that is used in heat exchanger one end in the prior art (the head pipe 11 or 14 among Fig. 2) is; All there is fluting 5 and 5 ' the outer wall both sides of middle size pipe 16; And the axis direction position of size pipe 16 is relative in relative two flutings, the 5 and 5 ' edge, and along the axis symmetry arrangement.I district and II district flat tube 12,17 are separately positioned in the fluting of both sides.Fig. 5 shows the local enlarged diagram that size pipe among Fig. 4 a 16 connects I districts and II district flat tube 12 and 17.
Heat exchanger shown in Fig. 4 a can change the import A of cold-producing medium and export the C position, reaches the flow direction that changes cold-producing medium, specifically shown in Fig. 4 b and Fig. 4 c.
Shown in Fig. 4 b, show the flow schematic diagram of the heat exchanger cold-producing medium when refrigeration among Fig. 4 a.At heat exchanger is under the cooling condition; When this heat exchanger served as condenser, the refrigerant gas of HTHP got into heat exchanger from the import A of upper head pipe 11, passes through upper head pipe 11 successively; I district flat tube 12; Middle size pipe 16, II district flat tube 17 and lower head pipe 14 leave heat exchanger through outlet C then.The cold-producing medium of HTHP is through I district flat tube 12 during with II district flat tube 17, through I district fin 13 and II district fin 15 with cold-producing medium with heat be discharged into and manage in the outer air, the cold-producing medium of HTHP becomes the liquid of cryogenic high pressure, the discharge heat exchanger.
Shown in Fig. 4 c, show the flow schematic diagram of the heat exchanger cold-producing medium when heating among Fig. 4 a.Under the cooling condition shown in above-mentioned Fig. 4 b; Heat exchanger as condenser; Its inlet tube and outlet are exchanged; Promptly changed the flow direction of cold-producing medium, made it be transformed to the evaporimeter under the heating condition, be i.e. the flow schematic diagram of cold-producing medium during heating shown in Fig. 4 c from the condenser under the cooling condition.When heating, the cold-producing medium of two phase low pressure gets into heat exchanger from the inlet C of lower head pipe 14, successively through lower head pipe 14, II district flat tube 17, and middle size pipe 16, I district flat tube 12 and upper head pipe 11 leave heat exchanger through outlet A at last.When two phase low pressure refrigerants pass through I district flat tube 12 with II district flat tube 17, the heat in I district fin 13 and the II district fin 15 absorption tube extraneous airs, the evaporation of two phase low pressure refrigerants becomes low pressure refrigerant gas.
Under two kinds of working conditions shown in above-mentioned Fig. 4 b and the 4c; Because cold-producing medium is built up during size pipe 16 in process again; And be assigned to once more in each root flat tube; Therefore the distribution of cold-producing medium in each root flat tube of after this flowing through is more even than micro-channel evaporator of the prior art, thereby performance is better.
Shown in Fig. 4 d, show the flow schematic diagram of the heat exchanger cold-producing medium when defrost among Fig. 4 a.When heat exchanger when carrying out defrost, high-temperature high-pressure refrigerant gas gets into heat exchanger, through the heat release of cold-producing medium own, makes the frost melts of heat exchanger surface.Shown in Fig. 4 d; The refrigerant gas of HTHP from upper head pipe 11 with two inlets of A, B of size pipe 16 get into heat exchanger simultaneously; The cold-producing medium that gets into from A gets into I district flat tube 12 after through the distribution of upper head pipe 11, size pipe 16 in flowing into later on extraneous heat exchange through flat tube 12 outer I district fins 13, with from the refrigerant fluid of the B entering that enters the mouth converge in the size pipe 16 after; The II district flat tube 17 of flowing through together again; Carry out heat exchange through flat tube 17 outer II district fins 15 with the outer air of pipe this moment, until flowing into lower head pipe 14, at last from C outlet outflow heat exchanger.Because getting into the refrigerant temperature of heat exchanger compares higher from the B inlet with the cold-producing medium that the I district flat tube 12 of flowing through carried out heat exchange; Therefore when the serious heat exchanger the latter half of cold-producing medium inflow frosting that flows into from the B inlet; Just during II district flat tube 17, can improve the defrost effect greatly and shorten defrost periods.
As shown in Figure 6, be the structural representation of the another kind of improved embodiment of micro-channel heat exchanger according to the present invention.
In this embodiment, the structure of the I district, heat exchanger top of being separated by middle size pipe 16 and the fin 13 in bottom II district and 15 is identical, but adopts different fin densities to arrange.As shown in the figure, for example, the density of the fin 13 in top I district is along 20～23 slices/inch of the length directions of flat tube, and the density of the fin 15 in bottom II district is along 16～20/ inches of the length directions of flat tube.When this heat exchanger serves as the evaporimeter of heat pump and have condensed water to produce; Because the effect of gravity, condensed water can drip downwards along flat tube, so many condensed waters can be gathered in the bottom of heat exchanger; Thereby influence increases windage and influences heat exchange, and causes the deterioration of frosting situation.After adopting the structure that changes fin density, II district in bottom is difficult for resting in the fin slit, thereby the discharging of condensed water is improved because the fin gap is bigger, and condensed water is smaller in the surface tension that receives, and also can play a role in improving to frosting simultaneously.
In the heat exchanger of the foregoing description since heat exchanger up and down two-part flat tube is separate with fin, therefore can take different forms and collocation, promptly different flat tubes and the collocation of different fins are to improve performance and to meet the different needs.
With reference to shown in Figure 7, show I district flat tube 12 and second kind of distribution schematic diagram of II district flat tube 17 in the heat exchanger of the present invention.Heat exchanger I district flat tube 12 is identical with II district flat tube 17 structures, and the distance in the distance in the flat tube 12 in I district between the adjacent flat tube and the II district flat tube 17 between the adjacent flat tube is also identical.Being provided with different with head pipe shown in Figure 5 and flat tube is that in the present embodiment, fluting 5 and the 5 ' stagger arrangement of middle size pipe 16 both sides are arranged, i.e. dislocation arrangement.As shown in Figure 7, the fluting 5 of middle size pipe 16 both sides is different with the position of size pipe 16 axis directions in the 5 ' edge, is interspersed.The advantage of this design be when cold-producing medium from I district flat tube 12 flows into during size pipe 16; Can be through confluxing in middle size pipe 16; Branch to again in each flat tube 17 of II district, rather than directly spray in the II district flat tube 17, thereby it is more even that cold-producing medium is distributed in the bolt for fastening a door from outside pipe in I district and II district.Fig. 7 has been merely and I district and II district flat tube has been described in the staggered position of middle size pipe 16 axis directions, and I district and the staggered position of flat tube, II district are not limited to the arrangement mode of flat tube illustrated in fig. 7, as long as stagger each other.
With reference to shown in Figure 8, show I district flat tube 12 and the third distribution schematic diagram of II district flat tube 17 in the heat exchanger of the present invention.In this embodiment; I district flat tube 12 adopts different spacing to arrange with II district flat tube 17; The spacing of adjacent flat tube is greater than the spacing of adjacent flat tube in the I district flat tube 12 in the II district flat tube 17, and the ratio of the spacing of II district flat tube 17 and I district flat tube 12 spacings changes in 1.2～2 scopes.This arrangement mode has promptly increased the gap between flat tube through the spacing that increases II district flat tube 17, thereby improves the condensed water drainage performance of heat exchanger bottom when heating, and is that condensed water has bigger space drainage to go out.
Shown in figure 9a and Fig. 9 b, show I district flat tube 12 and the 4th kind of distributed architecture sketch map of II district flat tube 17 in the heat exchanger of the present invention.In this embodiment, the flat tube of heat exchanger adopts design wide at the top and narrow at the bottom, and shown in Fig. 9 a, I district flat tube 12 adopts different widths with II district flat tube 17, i.e. the width of the flat tube 12 of I district employing is greater than the width of II district flat tube 17.For example, the width of the flat tube 12 that the I district adopts is 25 millimeters, and II district flat tube 17 width are 18 millimeters; Perhaps I district bolt for fastening a door from outside pipe width 12 is 18 millimeters, and II district flat tube 17 width are 12 millimeters.Fig. 9 b is the stereogram of the schematic side view of flat tube distribution shown in Fig. 9 a.The variation of this flat tube width; Make heat exchanger when the running refrigerating operating mode, because reducing of II district flat tube 17 width causes reducing of II district flat tube 17 internal refrigeration storage agent circulation areas; Cold-producing medium flow velocity in the II district flat tube 17 is improved, thereby the heat exchange property of II district flat tube 17 is improved.
When heat exchanger operation heating condition, the general main bottom that concentrates on of condensed water is the II district, so the bottom of heat exchanger can have bigger air drag in the prior art; The air of flowing through can be seldom, and heat exchange property is poor, and after narrower flat tube is adopted in the bottom of heat exchanger in the present embodiment (being the II district); The air drag that this body structure caused can decrease than top, thereby the air of the heat exchanger outer surface of flowing through is increased, and makes the air velocity more even distribution of heat exchanger surface; Improved heat exchange property; Simultaneously, the mass rate of emission of condensed water has been quickened in the raising of heat exchanger bottom air velocity again.
Figure 10 a and Figure 10 b show the sketch map that has the fin of different in width according to I district flat tube in the heat exchanger of the present invention 12 and II district flat tube 17.In this embodiment, the width of I district fin 13 employings is greater than the width of II district fin 15.Width described here be as shown in the figure with the orthogonal direction of flat tube length direction on transverse width W.For example, the width that I district fin 13 adopts can be 25 millimeters, and the width of II district fin 15 is 18 millimeters, 18 millimeters of the width of perhaps I district fin 13 employings, and fin 15 employing width in II district are 12 millimeters fin.The width of fin can be consistent with the spacing distance of adjacent flat tube, also can be inequality.The increase of spacing can make the condensed water in II district flow out smoothly between the II district fin like this, rather than condenses upon on the II district fin, has further improved the heat exchange property of heat exchanger.
Except aforesaid method of regulating cold-producing medium flow velocity in heat exchanger through the arrangement of regulating flat tube and fin, the present invention also provides through regulating the open-celled structure and the big or small flow velocity that changes cold-producing medium in the flat tube.Shown in figure 11a and Figure 11 b, show flat tube configuration sketch map with two kinds of different perforate types.Flat tube shown in Figure 11 a adopts bigger aperture, for example, and can be as the I district flat tube 12 of heat exchanger; Flat tube shown in Figure 11 b adopts and compares less aperture with shown in Figure 11 a, for example, and can be as the II district flat tube 17 of heat exchanger.The form of flat tube perforate can be circle, rectangle, square or other any type of holes well known to those skilled in the art.When heat exchanger adopts the flat tube shown in Figure 11 a as I district flat tube 12; When adopting the flat tube shown in Figure 11 b as II district flat tube 17; Under the running refrigerating operating mode, be mainly refrigerant liquid in the II district flat tube 17, use with respect to the littler perforate in flat tube 12 apertures of I district; Can be so that the cold-producing medium flow velocitys in the II district flat tube 17 improve, thus heat exchange property is improved.
When heat exchanger operation heating condition, be full of the cold-producing medium of gas-liquid two-phase in the II district flat tube 17, its volume flow is smaller, so the less flat tube in aperture helps improving the cold-producing medium flow velocity, thus the coefficient of heat transfer of raising liquid and gas mixed zone; And when cold-producing medium got into I district flat tube 12, main composition had become gas phase, and volume flow ratio two phase times are big a lot, and top adopts large aperture design can effectively reduce the pressure drop of cold-producing medium when flowing through flat tube.
According to the present invention, can also regulate the heat exchange property of heat exchanger through the structure that changes fin itself.With reference to figure 12a and 12b, show the structural representation of two kinds of fins.The surface of the fin 7 shown in Figure 12 a is smooth, and the surface of the fin 7 shown in Figure 12 b has a plurality of windows, for example the form of shutter.With respect to the ganoid fin shown in Figure 12 a, the fenestration fin among Figure 12 b is because have bigger effective heat exchange area, so exchange capability of heat is stronger.Can adopt dissimilar fins to regulate the heat exchange property of heat exchanger through I district and II district at heat exchanger.For example, fin 12 is selected to use the common fenestration fin shown in Figure 12 b in the I district, and fin 17 selects to use the light fin shown in Figure 12 a in the II district.The fenestration fin can also be regulated heat exchange property through the angle that adjusting is windowed.The angle of windowing is big more, and the effective heat exchange area is big more; The angle of windowing is more little, and the effective heat exchange area is more little, when louver angle is reduced to 0 °, then is equivalent to the smooth fin shown in Fig. 2 a.For example, I district fin 12 can adopt the fin that louver angle is big among Figure 12 b, heat exchange property is high, and II district fin 17 adopts the little fin of louver angle among Figure 12 b, thereby improves condensed water drainage performance and frosting performance.Wherein, the louver angle transformation range of said fenestration fin is 0 °-90 °.Those skilled in the art also it is understandable that, the shutter form shown in here is an example, also can adopt other forms of windowing to realize regulating the heat exchanger heat exchange property.
Explanation through above embodiment; Those skilled in the art can change above-mentioned embodiment at an easy rate; For example two kinds of perhaps fins of number of different types are used in the zone, upper and lower; Perhaps the spacing between the adjacent fins in II district is arranged to greater than the spacing between the I district adjacent fins, to improve the heat exchange property of heat exchanger.
13a and 13b show the structure according to other a kind of heat exchanger of the present invention respectively.Figure 13 a is the side view of heat exchanger, and Figure 13 b is the stereogram of this heat exchanger.As shown in the figure, the both sides of the middle size pipe 16 of heat exchanger with the perpendicular direction of the length direction of flat tube on have outward extending sheet guiding gutter 18 respectively.Can find out that from Figure 13 b guiding gutter 18 has certain width, be laminated structure, extend with the direction of middle size pipe 16 axial almost parallels, its structure is similar to the eaves in house.Because during heat exchanger operation heating condition; Condensed water can flow by flat tube 12 along the I district on top vertically downward; Cause heat exchanger bottom (being the II district) to gather many condensed waters; Therefore middle size pipe 16 is designed to the special construction of the band guiding gutter 18 shown in Figure 13 a, it can gather the condensed water that top I district flat tube 12 flows down above that, and the smooth and easy discharge of condensed water is changed in guiding.
Figure 14 a and 14b show the heat exchanger structure that another kind has the middle size pipe 16 of guiding gutter 18, and wherein Figure 14 a is the side view of heat exchanger, and Figure 14 b is the front view of heat exchanger.Be with the difference of the heat exchanger shown in above-mentioned Figure 13 a; The guiding gutter 18 of middle size pipe 16 is not a horizontal positioned, the axial direction of size pipe 16 in promptly being not parallel to, but certain gradient is arranged with respect to this axial direction; The angle of inclination is usually between 0 to 15 °; Thereby make condensed water can't accumulate on the size pipe 16, but can be, thereby played the effect of water conservancy diversion because of the downward smooth and easy discharge of the effect of gravity.
With reference to figure 15a and 15b, show the heat exchanger that another has the middle size pipe 16 of flow-guiding structure, wherein Figure 15 a is the side view of heat exchanger, Figure 15 b is the front view of heat exchanger.Shown in Figure 15 b, tilt certain angle is arranged according to the middle size pipe 16 of this embodiment axial direction with respect to upper head pipe 12 and lower head pipe, the angle of inclination is generally between 0 to 15 °.Middle size pipe 16 has guiding gutter 18 equally, and guiding gutter 18 is set to extend with the axis direction almost parallel of middle size pipe 16.According to this configuration of this embodiment, the condensed water that heat exchanger top is discharged, after converging on the middle size pipe 16, gravitate is discharged along the guiding gutter that tilts.
Through above explanation; Heat exchanger of the present invention can have multiple variation; For example can adopt the subregion of varying number, each subregion adopts different fin density, flat tube width, flat tube quantity, flat tube spacing and the flat tube configuration with multi-form perforate, in each changes; Can also adopt different fin types; For example the fin of smooth surface or surface have the fin of windowing etc., adopt two kinds of heat exchange property fins inequality to be used on the heat exchanger of zones of different, can realize that heat exchanger lower area of the present invention reduces the effect of condensed water gathering.Flat tube among the present invention, fin can be processed for traditional aluminum alloy materials, link technologies such as can adopting soldering, high-frequency welding between fin and flat tube, flat tube and the head pipe.
Micro-channel heat exchanger in the present embodiment is the new high-efficiency heat exchanger that a kind of whole employing aluminum alloy materials is processed; Compare with traditional finned tube exchanger, the performance of improved micro-channel heat exchanger on average can improve approximately about 30% according to the present invention, and the charging amount of unit cold-producing medium on average can reduce about 30%; Heat exchanger is all made through soldering by a kind of materials of aluminum; Not only be easy to reclaim, and avoided potential corrosion, can guarantee that therefore heat exchanger uses for a long time efficiently.
The present invention is illustrated through the foregoing description, but should be understood that, the foregoing description just is used for for example and illustrative purposes; But not be intended to the present invention is limited in the described scope of embodiments; In addition, it will be appreciated by persons skilled in the art that the present invention is not limited to the foregoing description; Can also make more kinds of variants and modifications according to instruction of the present invention, these variants and modifications all drop in the present invention's scope required for protection.Protection scope of the present invention is defined by appended claims book and equivalent scope thereof.
Claims (26)
1. micro-channel heat exchanger that is used for air-conditioning heat pump, said heat exchanger comprises, upper head pipe (11), lower head pipe (14), said upper head pipe (11) and said lower head pipe (14) are parallel to each other; The a plurality of flat tubes that are parallel to each other and separate (6) that connect said upper head pipe (11) and said lower head pipe (14), said flat tube (6) inside are provided with the perforate with said upper head pipe (11) and said lower head pipe (14) internal communication; Be arranged between the adjacent said flat tube (6) along a plurality of fins (13 of arranging on said flat tube (6) length direction; 15); It is characterized in that the length direction along said flat tube (6) reduces towards said lower head pipe (14) distribution density of said fin (13,15) gradually from said upper head pipe (14).
2. micro-channel heat exchanger as claimed in claim 1 is characterized in that said fin (13,15) is wavy arrangement along the length direction of said flat tube is end to end each other.
3. micro-channel heat exchanger as claimed in claim 1; It is characterized in that said fin (13,15) can be divided at least two zone (I according to the difference of distribution density; II); (I, II) length direction along said flat tube (6) reduces towards said lower head pipe (14) density gradually from said upper head pipe (14) in said at least two zones.
4. micro-channel heat exchanger as claimed in claim 1 is characterized in that said fin (13,15) is 16～23 slices/inch along the distribution density scope of the length direction of said flat tube (6).
5. micro-channel heat exchanger that is used for air-conditioning heat pump; This heat exchanger comprises; Upper head pipe (11), lower head pipe (14); Said upper head pipe (11) and said lower head pipe (14) are parallel to each other, and size pipe (16) in also comprising is positioned between said upper head pipe (11) and the said lower head pipe (14); And a plurality of first group of flat tube (12) that are parallel to each other and separate that connect said upper head pipe (11) and said middle size pipe (16), with a plurality of second group of flat tube (17) that are parallel to each other and separate that are connected said lower head pipe (14) and said middle size pipe (16); Said first group of flat tube (12) inside is provided with first group of perforate with said upper head pipe (11) and said middle size pipe (16) internal communication, and said second group of flat tube (17) inside also is provided with second group of perforate with said lower head pipe (14) and said middle size pipe (16) internal communication; And be arranged between adjacent said first group of flat tube (12) along first group of fin (13) of arranging on said first group of flat tube (12) length direction; And be arranged between adjacent said second group of flat tube (17) along second group of fin (15) of arranging on said second group of flat tube (17) length direction; Wherein, the distribution density of said first group of fin (13) is greater than the distribution density of said second group of fin (15).
6. micro-channel heat exchanger as claimed in claim 5 is characterized in that said middle size pipe (16) is that said upper head pipe (11) is to 1/2nd or 1/3rd of said lower head pipe (14) spacing apart from the distance of said upper head pipe (11).
7. micro-channel heat exchanger as claimed in claim 5; It is characterized in that when said heat exchanger is operated in cooling condition; Cold-producing medium gets into said heat exchanger from said upper head pipe (11), and passes through said first group of flat tube (12), said middle size pipe (16) and said second group of flat tube (17) successively and discharge from said lower head pipe (14).
8. micro-channel heat exchanger as claimed in claim 5; It is characterized in that when said heat exchanger is operated in heating condition; Cold-producing medium gets into said heat exchanger from said lower head pipe (14), and passes through said second group of flat tube (17), said middle size pipe (16) and said first group of flat tube (12) successively and discharge from said upper head pipe (11).
9. micro-channel heat exchanger as claimed in claim 5; It is characterized in that when said heat exchanger is operated in the defrost operating mode; Cold-producing medium from said upper head pipe (11) and said size pipe (16) get into said heat exchanger simultaneously, in said, converge in the size pipe (16) after said second group of flat tube (17) discharged from said lower head pipe (14).
10. micro-channel heat exchanger as claimed in claim 5 is characterized in that said first group of fin (13) and said second group of fin (15) are 16～23 slices/inch along the distribution density scope of the length direction of said first group of flat tube (12) and said second group of flat tube (17) respectively.
11. micro-channel heat exchanger as claimed in claim 5 is characterized in that the be staggered both sides of in said size pipe (16) of said first group of flat tube (12) and said second group of flat tube (17).
12. micro-channel heat exchanger as claimed in claim 5 is characterized in that the spacing between the adjacent flat tube is less than the spacing between the adjacent flat tube in said second group of flat tube (17) in said first group of flat tube (12).
13. micro-channel heat exchanger as claimed in claim 5, it is characterized in that said first group of flat tube (12) perpendicular to the width on its flat tube length direction greater than said second group of flat tube (17) perpendicular to the width on its flat tube length direction.
14. micro-channel heat exchanger as claimed in claim 5, it is characterized in that said first group of fin (13) perpendicular to the width on the said flat tube length direction greater than said second group of fin (15) perpendicular to the width on the said flat tube length direction.
15. micro-channel heat exchanger as claimed in claim 5 is characterized in that the aperture of the aperture of said first group of perforate greater than said second group of perforate.
16. micro-channel heat exchanger as claimed in claim 5, what it is characterized in that said first group of perforate and said second group of perforate is shaped as circle or rectangle.
17. micro-channel heat exchanger as claimed in claim 5, the surface that it is characterized in that said first group of fin (13) and said second group of fin (17) are smooth or are provided with a plurality of windowing.
18. micro-channel heat exchanger as claimed in claim 17 is characterized in that the surface of said first group of fin (13) is provided with a plurality of windowing, the surface of said second group of fin (17) is smooth.
19. micro-channel heat exchanger as claimed in claim 17 is characterized in that the said angular range of windowing that is provided with on the said fin is 0 ° to 90 °.
20. micro-channel heat exchanger as claimed in claim 17; It is characterized in that being provided with a plurality of windowing on said first group of fin (13) and the said second group of fin (17), said first group of fin (13) gone up the louver angle that is provided with and gone up the louver angle that is provided with greater than said second group of fin (17).
21. micro-channel heat exchanger as claimed in claim 5 is characterized in that the both sides of said middle size pipe (16) are respectively arranged with outward extending guiding gutter (18) on the direction vertical with the length direction of said first group of flat tube (12).
22. micro-channel heat exchanger as claimed in claim 21 is characterized in that the direction extension of the axial almost parallel of said guiding gutter (18) edge and said middle size pipe (16).
23. micro-channel heat exchanger as claimed in claim 5; It is characterized in that said in size pipe (16) both sides with said in be respectively arranged with outward extending guiding gutter (18) on the direction of axially parallel of size pipe (16), and said middle size pipe (16) axially with respect to the certain angle of axioversion of said upper head pipe (11).
24. micro-channel heat exchanger as claimed in claim 5 is characterized in that the both sides of said middle size pipe (16) are respectively arranged with outward extending guiding gutter (18) on the direction of the angle certain with respect to the axioversion of size pipe (16) in said.
25., it is characterized in that said micro-channel heat exchanger processed by aluminum alloy materials like claim 1 or 5 described micro-channel heat exchangers.
26., it is characterized in that being connected through soldering or high-frequency induction welding technique between said fin and said flat tube and said flat tube and said upper head pipe, middle size pipe or the lower head pipe like claim 1 or 5 described micro-channel heat exchangers.
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| CN200910157622A CN101963418B (en) | 2009-07-21 | 2009-07-21 | Micro channel heat exchanger for air-conditioner heat pump |
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| CN200910157622A CN101963418B (en) | 2009-07-21 | 2009-07-21 | Micro channel heat exchanger for air-conditioner heat pump |
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| CN101963418B true CN101963418B (en) | 2012-09-05 |
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